Hydraulic motor for rotary spindle machines



Nov. 9, 1937. E. K. BENEDEK HYDRAULIC MOTOR FOR ROTARY SPINDLE MACHINES Filed June 7, 1935 4 sheets-sheet 1 Rm mk 4 om.

Nov. 9, 1937. E. K. BENEDEK V HYDRAULIC MOTOR FOR ROTARY SPINDLE MACHINES 4 Sheets-Shet 2 Filed June 7, 1935 K. E D E N E nu. K K u L 9, 1937. E. K. BENEDEK I HYDRAULIC MOTOR FOR ROTARY SPINDLE MACHINES xmms Filed June '7, 1935 4 Sheets-Sheet 3 E. K. BENEDEK HYDRAULIC MOTOR FOR ROTARY SPINDLE MACHINES Filed June 7, 1935 4 Sheets-Sheet 4 i 51.06 06 m .Irv/M I 102 EELZ ELEKKBENEDEK- Patented Nov. 9, 1937 UNITED STATES PATENT OFFICE HYDRAULIC MOTOR FOR ROTARY SPINDLE MACHINES 32 Claims.

This invention relates to rotary spindle machines and particularly to a hydraulic radial plunger motor and spindle combination for use in connection with high speed precision rotary spindle turret lathes and like machinery.

One of the principal objects of the present invention is to provide a motor of this character having as an integral part of the motor barrel a hollow rotary spindle. l

An equally important object is yto effect torque transmission to the spindle without creating lateral unbalanced forces thereon due to the transmitted load.

Still another object is to provide a motor of this character having a greater range of speed and torque, and in which the increments of speed and torque may be infinitesimal Vso that gradually and uniformly increased and decreased speeds and torque delivery may be provided during the operation of the spindle and throughout the entire range and at constant horsepower output, and the usual abrupt changes in speed and torque delivery are eliminated.

A more specic Objectis to provide a combination motor and spindle machine mounting incorporating the machine, the hydraulic motor and operating pump therefor so as to effect the results desired with a minimum of space requirements and accessory parts.`

Another object is to provide a new and improved hydraulic pump or motor structure.

A correlative object is to provide a spindle machine capable of operating at high speed and torque for long sustained intervals'of time and in which misalignment or eccentricity of the spindle due to severe lateral thrusts and resultant wear is eliminated.

Other objects and advantages will become apparent from the following specification wherein reference is made to the drawings in which Fig. 1 is a horizontal longitudinal sectional view of a hydraulic motor 'and spindle combination for use in connection with the present invention, and

J is taken on a plane indicated by the line l-I of Fig. 4;

Fig. 2 is a vertical-sectional View taken on a plane indicated by the line 2 2 in Fig. 1;

Fig. 3 is a sectional view of the motor valve ino sert of Fig. 2 and is taken on a plane indicated by the line 3 3 of Fig. 2.

Fig. 4 is a front elevation of a turret lathe embodying the principles of the present invention, a portion of the casing being removed'for clearness 5 in illustration;

Fig. 5 is a front elevation of one of the operating parts of the driving mechanisms.

Fig. 6 is a side elevation, partly in section, of a combination hydraulic motor and spindle assembly providing a modification of the present 5 invention, and illustrating certain eiects produced by the conventional spindle drive; and

Fig. 'l is a front elevation, partly in section, of a dual machine embodying the present invention.

For convenience in illustration, the principles 10 of the present invention are shown embodied in a turret lathe of the high speed and high torque precision type, the utilization of the spindle in other types of machines being readily apparent therefrom, and it is not meant to limit the ln- 15 vention to this specific application, this use being merely one adaptation thereof.

Heretofore, in lathes and machines of this character, the.practice has been to mount the spindle in expensive roller bearings which were 20 sufficiently heavy to anti-frictionally mount the spindle and at the same time to resist lateral thrusts delivered by the driving gears. 'I'he drive of the spindle was effected by a number of main gears mounted directly on and coaxial with the spindle, these gears being of different sizes. In order to provide an appreciable number of speed changes, a large number of gears and countershafts were utilized, and it Was necessary that these also be mounted to withstand lateral or 30 radial thrusts aswell as axial thrusts. These large and complicated gear trains were driven selectively from a main shaft in regard to whichthe same `problems were presented. Accurate and durable anti-friction clutches were provided for 35 selectively engaging predetermined gears of the driving shaft with certain gears of the countershafts and spindle through the medium of the intervening gear trains. In many instances, additional clutches were interposed for selectively 40 combining different gears of the countershafts. Such equipment requires a large amount of space for its accommodation and, in addition, a complicated system of levers and calibration plates showing the different speeds for different settings. In some instances a dual speed electric motor was used for doubling the number of speeds obtainable. Thus, aside from the large and expensive equipment and wasted space and the inertia of a large number of moving parts necessary to be shifted and changed in speed, the speed can be changed only in increments or stages each of which increments provided an abrupt and considerable increase or decrease over the one preceding or succeeding.

Great disadvantages reside in the fact that a large number of moving parts are all subject to wear with resultant noise, jerky operation, inaccuracy, and ineiiiciency. The gears necessarily exerted terrific thrusts on the spindle in effecting torque transmission thrusts and these thrusts were so directed as to tend to displace the spindle radially from its proper operating position. Continued unbalanced load of this character soon creates such wear that precision in the position of the spindle axis is destroyed and in a short while the spindle is so misaligned or offset from its original accurate position that a reasonable degree of accuracy can no longer be obtained, whereupon, the entire spindle driving connections, mountings, and expensive anti-friction bearings, in addition to the necessary bushings and co operating parts, must be replaced.

In the present invention, the spindle is relieved from severe unbalanced loads created by torque transmission. Furthermore, the wear of most of the driving parts of the present structure is such as not to affect appreciably the alignment of the spindle and rotation thereof about its original axis of rotation. Again, the change in torque or speed of the spindle can be obtained with the present small and compact structure by means of two control levers, each of which may be operated independently, or, for slight changes in speed, one only need be operated at any given time, and eiiicient results can be obtained. 'Ihese results are obtained by the present structure without any addition to, but, in fact, with elimination of a large number of sets of expensive anti-friction rollers required in previous structures.

Referring first to Figs. 1 and 4, a hydraulic radial piston motor and spindle combination combined with a turret lathe is shown for purposes of illustration. The entire structure comprises a combination supporting base and housing I, in and on which the cooperating parts are mounted. The combination base and housing I includes a iloor 2, and integral side walls 3 and end walls 4 which form a sump for receiving slip uid .from the hydraulic mechanism.

Mounted on the oor 2 of the housing is an electric motor 5 of the double end drive shaft type. To one end of the motor shaft is directly connected a pump 6 of a reversible hydraulic transmission Which` is comprised of the pump 6 and a motor 'I, the transmission combination being such as described in my copending application Serial No. 5,429, i'iled February '7, 1935. Both the pump 6 and motor 'I are provided with adjustable reactances which may be operated by control rods 8 and 9 respectively for controlling the speed and torque delivery of the motor 'I. The turret of the lathe is drivingly connected to the motor 'I through the medium of a shaft II and belt I2 and outer end of the shaft I1 which, in turn, drives the usual mechanism provided in the 'turret support I0 at the speeds desired.

A suitable hand Wheel I3 is provided for manual operation of the support I0. The usual tool support I4 is provided on the' lathe, the hand wheel i5 being provided and cooperating with the rack I5a for adjustment of the tool to the desired position along the housing. The turret on the support l0 also is arranged for driving in the usual manner by a mechanical transmission I6 drivingly connected thereto through the medium of the shaft I'I for thread cutting and similar operations. The mechanical transmission I 6 is provided with a hand operated clutch I 8 so that either it or the hydraulic transmission motor 'I may be utilized for effecting the driving relation. The transmission I6 is driven from the end of the motor 5 opposite from the hydraulic transmission, as illustrated in Fig. 4.

Mounted within the casing is a hydraulic radial .plunger variable delivery pump 20 which is directly driven by the opposite end of the shaft of the electric motor 5 and which supplies the hydraulic pressure uid to the hydraulic motor Which drives the spindle of the machine. The delivery of the pump 20 may be controlled by suitable control rods 2|, the pump preferably being such as described in my copending application, Serial No. 721,961, filed May 22, 1934. Hydraulic fluid is supplied to the pump from the sump formed by the floors and Walls of the housing I through a suitable suction conduit 22 and is discharged. from the pump through a pressure conduit 23 to the spindle driving hydraulic motor, designated generally at 25. A low pressure con- Iduit 26 is connected to the motor 25 and discharges into the interior of the casing, thus completing the hydraulic circuit.

'Ihe spindle motor 25 is preferably of the reversible, variable speed multi-stage type of the general character described in my copending application Ser. No. 31,651, nled July 16, 1935, comprising a plurality of separate stages, each of which is adjustable independently of the other. In the form illustrated, two stages are provided, these stages corresponding in size to the stages of the motor housing. For example, the motor housing may comprise an enlarged portion 21a and a s'maller diameter portion 2lb. The motor pintle and the valve connection between the pintle and the motor stages which form part of the hydraulic circuit are mounted in a housing 28 which may be formed integralwith the end wall 4 of the lathe housing I, the housing 28 having a large radial ilange 29 which is, in effect, a portion of the end wall 4 of the housing I and provides the end wall of .the housing portion 21a.

In turret lathes and other spindle machines of this character, it is necessary that a passage be provided through the spindle for accommodatingthe piece of work being operated upon. .The

present motor provides for effective valving cooperation between the hydraulic cylinders of a motor barrel which is combined with a spindle coaxial with the' barrel of the motor, the spindle and barrel having an axial passage extending entirely therethrough for accommodating the Work axially. Referring particularly to Fig. 1, a multi-stage hydraulic motor is illustrated. The motor comprises a barrel 30 havingat one end a reduced diameter annular hub 3| on which is press fitted an inner bearing race for mounting the end of the barrel in anti-friction rollers 32. The outer race of the rollers 32 is press fitted into the bore of the housingportion 28 heretofore described so as to support the barrel therein in coaxial relation to the housing. At the opposite end of the barrel 30 is a reduced annular hub portion 33 by which, through the medium of a suitable inner race, the barrel is anti-frictionally supported on roller bearings 34, the cooperating outer race oi which is mounted in the housing portion 21e. The bearings 32 and 34 are preterably 'Iyson" tapered rollers and are arranged to resist both radial and laxial loads and thrusts. 'Ihe hul)v portions 3l andl oi' the barrel extend outwardly beyond the corresponding ends oi' the motor housing and form the end portions of the lathe spindle which is designated generally as 36. The barrel is provided with an axial bore 31 of proper size to accommodate the work piece to be operated upon. The bore 31 is coaxial with the rotational `axis of the barrel andextends axially to the ends of the spindle 36 and is open at the ends. The spindle carries at one end a chuck 31 for the Work piece or tool. In this manner a unitary coaxial barrel and spindle is provided.

Intermediate the hub portions 3| and 33 of the barrel, the barrel has a. large diameter portion 38 and a reduced diameter portion 39, which portions form different stages of the motor respectively. The barrel portions 38 and 39 are provided with radial flanges 40 and 4| respectively. In the barrel portion 38 are'radial cylinders 44, the cylinders being arranged in two sets spaced axially of the barrel, and the cylinders of each set being spaced circumferentially from each other. Correspondingly, the barrel portion 39 is provided with a set of circumferentially spaced radial cylinders 46. The cylinders 44-are arranged in pairs, one cylinder from each set -being in the same pair. The two cylinders of the same pair have their axes in the same radial plane through the rotational axis of the barrel. The cylinders 46 correspond in number to the pairs of cylinders 44 and have their axes in the corresponding ones of said planes. Beginning at the junction of the hub portion'33 and the portion 39 of the barrel, suitable longitudinally extending ducts 41 are formed, one duct for each pair of cylinders 44 and corresponding cylinder 46. Since the cylinders are aligned axially of the barrel, as described, the ducts 41 may be' drilled from one end. The ducts 41 extend beyond the end of the portion 38 of the barrel and terminate in a reduced diameter valve portion 49, formed on the barrel between the hub 3| and the portion 38 of the barrel. The ducts 41 connect respectively with radial ducts 50 which open through the valve surface of the portion 49 of the barrel. Mounted within the motor casing portion 28 and aligned radially with the portion 49 oi thebarrel is avalve port insert 5| having a high pressure port 52 and a low pressure port 53 for successively communicating the cylinders of the barrel with the high and low pressure fluid conduits of the system as the barrel rotates.

Between the ends of the ports 52 and 53, the insert is provided with bridge positions 54 and 55 which snugly t over the valve portion of the barrel and form the intercepting bridges between the high pressure and low pressure ports, and block the cylinder ducts or ports 5|) as the ports are aligned therewith during rotation of the barrel. The circumferential walls of the ports 52 and 53 are preferably arcuate about an axis parallel to the axis of the insert but offset therefrom at right angles to the bridges so that the ports may be formed readily and accurately. 'Ihus upon the rotation of the barrel 30,- the cylinders, through the medium of their corresponding ducts 41 and 56, are successively communicated with the high pressure fluid port 52 and then discommunicated therefrom and communicated with the low pressure port 53.

The high pressure uid port 52 is connected with the high pressure conduit 23 of the hydraulic pump 20 and the low pressure port 53 is connected by the conduit 26 with thev fluid sump in the housing In order to effect rotation of the barrel by the hydraulic fluid, each of the cylinders 44 is provided with a radial plunger 66 which is reciprocable radially of the barrel. Correspondingly, the cylinders 36 are provided with plungers 6|.

The plungers 66 are arranged in pairs and cooperate with a common adjustable reactance stator 62 which is mounted in the casing portion 21a., with its axis parallel to the rotational axis of the barrel, for adjustment to different positions to dispose the axis of the reactance stator eccentric but parallel to the axis of the barrel. Suitable adjusting rods 63 which may be operated by hand or by a suitable control such as described in my co-pending application Serial No. 749,746 filed October 24, 1934 are provided for shifting the reactance. The rods 63 extend through the` casing 21a and are accessible from the exterior for operation. In order to cooperate each pair of plungers 60 and the reactance stator 62, each of the plungers 60 is provided with a head 64 which is shown integral with the associated plunger. Each plunger head 64 has a pin receiving bore extending parallel to the rotational axis of the barrel, vthe bore being counter bored intermediate its ends to form a lubricant retaining trough in which are disposed capillary cageless needle rollers 65. 'I'he bores of the plungers 60 of each pair are aligned axially of the barrel and in each pair is rotatably mounted and supported, by the bearings 65, a thrust pin 66 which is common to both plungers 60 of the pair. The thrust pin 66 extends axially beyond the outwardly disposed faces of the heads 64. Intermediate the heads and the corresponding outermost ends of the pin, the pin has reduced diameter portions 61 which form races for capillary cageless needle rollers.68.

Mounted on the rollers 68 are reactance engaging load transmitting rollers 69 which are constrained to position axially by the adjacent faces of heads 64 and radial shoulders 62a on the stator 62. For retaining the needle rollers 68 in proper operating position relative to the rollers 69, the outermost end portions of the pins 66 are provided with circumferential recesses 10 in which are snap fitted annular retaining springs 1| 'Ihe end portions of the pins 66 outwardly beyond the springs 1| engage suitable annular circumferentially floating rings 15 for assuring positive maintenance of the rollers 69 with respect to the reactance stator 62, the rings 15 being provided with annular grooves on the radially outer surface to accommodate the springs 1|, as indicated at 15a. The plungers 6| are provided with cross pins 16 rotatably mounted in needle rollers 11 in the plunger heads. Correspondingly, portions of the pins 16 form races accommodating needle rollers 18 for rotatably mounting the reactance rollers 19. Floating rings, similar in form and function .to the rings 15, also are provided. Thus, in both instances, the cross pins may rotate about their own axes relative to the plunger heads with which associated and independently of the associated rollers. The rollers 69 and 19, in turn, may rotate about the axis of the associate pins independently of the rotation of the associated pins. Thus the rotational speed of the rollers relative to the surface of the associated pins and of the pins relative to the associated plunger heads is materially reduced andv Wear and heating is substantially eliminated.

The plungers 6| cooperate vwith an adjustable reactance 8U which is shifted by suitable control rods 8|, the reactance and control rod corresponding in function to the reactance 62 and control rods 63.

As heretofore mentioned, the pump is a reversible variable displacement pump and the stroke and delivery may be controlled accurately. Since both stages of the motor may be indepe ently controlled substantially any torque or s d required at a constant horsepower delivery may be obtained and the motor operated throughout a greater range at higher eiiiciencies than in the case of a single stage motor.

For eiecting these advantages and maintaining the proper axial alignment of the spindle of the apparatus, only two sets'of roller bearings 32 and 34 are required, and these constrain both barrel and spindle to xed axial and radial position. Obviously, wear in the other parts of the motor, while aiecting the eiiiciency of` output, does not aiect the axial alignment of the spindle. In case of undue wear all that is required is that the sets of rollers 32 and 34 be removed from the casing and replaced and thereupon the perfect alignment of the spindle is'again assured. Thus the bearings 32 and 34 serve both as the barrel and spindle bearings, dispensing with several .expensive bearing, gear and clutch assemblies. The bore of the insert 5| and corresponding valve surface 49 of the barrel are so related as to insure an oil film for equalizing the hydraulic load imposed, and since the spindle is relieved from shifting driving gear thrusts, the accuracy of operation over long periods is assured. Substantially no axial thrust is imposed.

As above mentioned, a hydraulic transmission may be drivingly connected to the standard spindle of a machine. vReferring to Fig. 6, such a spindle is indicated at and is rotatably mounted at its' ends, preferably in suitable antifriction roller bearings, not shown. Mounted on the spindle 85 is a helical gear 86 for driving the spindle, the gear 86, in turn, being driven by a suitable idler gear 81 which, in turn, is driven by a gear 88 mounted .on the drive shaft 89 of a hydraulic transmission. The hydraulic transmission is preferably of the type described in my co-pending application Ser. No. 5.4291ed February 7, 1935, comprising a variable speed radial plunger motor and a variable delivery rotary radial plunger pump 9|, the pump being driven from a suitable source of power through a pulley 92. The reactances of the motor and pump respectively may be adjusted by suitable hand Wheels operating the adjusting rods 93 and 94 respectively. In this type of structure, however, it is apparent that a large thrust is transmitted by the gear 88 in a direction indicated by the arrow a, this force being withstood by a reactionary force in the mounting of the transmission, indicated by the arrow b.`This induces on the gear 86a force directed as indicated 'by the arrow c which must be withstood by the reactionary force of the bearings, as indicated by the arrow d.

While the structure illustrated in Fig. 6 re.

quires far less room and number of working parts than the mechanical gear connection and permits far greater ranges of speed and torque at constant horse power output and accurate adjustment, it nevertheless imposes lateral forces on the spindle which tend tocause wear of the spindle bearings and misalignment of the spindle.

Referring briefly to Fig. '7, another eifective installation is illustrated. This installation is particularly adapted for those instances in which spindles are provided for engaging opposite ends.

of the work. In the form illustrated, the lathe is mounted in a casing |0| corresponding to the casing I, heretofore described. Within the casing |0| there is provided a continuous ange |02 forming a sump for slip fluid. Mounted on the iioor of the casing 0| within the limits of the ange |02 is an electric motor |03 drivingly connected to a radial plunger variable delivery pump |04. The pump |04 is connected on the suction side -to the sump through a conduit |05. Leading from the pressure side of the pump is a conduit |06 which is connected in parallel with two adjustable variable delivery multi-stage hydraulic motors |01 and |08, such as above rst described. Each of the motors |01 and |08 is provided with a hollow spindle corresponding to the spindle 36 which, in eiect, is a part of and integral with the barrel of the associated motor. These spindles, indicated at |09 and ||0 respectively, are coaxial with respect to each other. The circuit is completed by discharge conduits and ||2 leading from the motors respectively to the sump in the casing |0|. Valves ||3 and ||4 are connected in the line |06 for rendering the motors selectively operable as single spindle machines when desired.

,maintaining accurate alignment of the spindle,

the bearings 32 and 34 are adjustable with respect to each other for taking up wear or radial slackness. Referring to Fig. 1, the casing portion 28`is closed at the end by an end plate 28a having an axially extending boss portion 28h engaging the end ofy the outer race of bearings 32. By merely loosening the plate 28a and inserting proper shims between it and the end wall of the casing 28 and then drawing the plate 28a firmly into position, the bearings 32 and 34 are adjusted relatively and properly axially of the barrel. Adjustments to one one-thousandth of an inch are made possible by this arrangement.

By virtue of the hydraulic transmission provided by the pump 6 and motor 1, acting through the shaft Il, beltl I2 and shaft (see Figs. 1 and 5), the turret can be moved very rapidly when it must be changed from one position to a remote position. Again, by varying the displacement of the pump 20, utilizing the spindle motor as av constant stroke motor, a wide range of torque and speed is obtained. Adding to this the use of the variable speed characteristics of the motor 25, a wide range is provided for any adjustment of the pump 20 and independently of the adjustment of the pump. By the conjoint use, a constant horsepower delivery prime mover such as the motor 5 can be made to provide an innite range of speeds and torque.

In order to better illustrate the constant horsepower cycle obtainable with the present structure,

it Ashould be noted that the motor 5 may be constant horsepower output. The motor 20, when operating at its maximum stroke at a predetermined pressure, likewise provides a' constant horsepower delivery. This horsepower may be utilized at all speeds of the spindle. For example,

` barrel and spindle, and means yfor supplying prescapacity of forty times that -oi'the smaller stage when it is set at full stroke, the speed of the spindle will be reduced to one fortieth of the speed provided by the smaller stage. The torque, howis forty times less than were the small stage of the motor operating.

If an extremely high speed is required, the smaller stage of the spindle motor may be operated at full eccentricity or stroke and the larger stage set at zero so that all of the output of the pump is utilized in the small stage.' Thus. the actual torque will be greatly reduced but the speed greatly increased resulting, however, in the same horsepower output to the spindle as that delivered by the pump. Assuming an underspeed is required, while the larger stage is operating at maximum stroke, the smaller stage may be added thereto, 'thus additionally reducing the speed of the spindle without aiecting materially the horsepower output. Again, if overspeed drive is required, the larger stage may be set at zero eccentricity and the stroke of the smaller stage set to less than maximum, and all ofthe pump output will be utilized at this overspeed. Thus at all times, the total horsepower output of the pump may be utilized. An even greater range of adjustment can be eiected by variations in the stroke of the pump 20.

Since both the pump 6 and motor 1 are of var-l iable delivery, obviously the speedof the shaft l1 can be varied throughout a wide range so that the tool can be fed slowly or rapidly, or, if desired, slowly in one direction or for part of its travel and rapidly for part of its travel. Likewise, if a rapid movement of the turret is desired after a given operation it can be eiected, or a rapid movement in one ,direction and slower movement in another may be eiected, depending upon the exigencies of the particular Work being done.

All the motors and pumps may be reversible, so that the combinations of torque, speeds, and directions of operations'of all the parts are iniinite. In case a reversible pump is used with the reversible motor the external circuit herein shown may be changed in the usual manner so that the external circuit may be reversed.

Having thus described my invention, I claim:

1. In a rotary spindle machine, a support, a rotary, radial plunger, hydraulic motor carried by said support, said motor comprising a rotatable barrel, radial cylinders therein, plungers reciprocable in the cylinders respectively and reactlance means for the plungers, fluid ducts in said barrel connected with said cylinders respectively, each duct being continuously in communication with its associated cylinder, said barrel having valve ports connected with ducts respectively, valve means in valving cooperation with said ports, said barrel having an axial bore coaxial with the axis of rotation of the barrel andA extending entirely therethrough from end to end,

and being open at the ends for accommodating the work piece tov be operated by the machine, a spindle having a Work piece accommodating passage open at both lends and coaxial with the barrel passage, vmeans drivingly connecting the sure iiuid to said motor for driving the same.

2. In a rotary spindle machine, a support, a rotary, radial plunger, hydraulic motor carried by said support', said motor comprising a rotatable barrel, radial cylinders therein, plungers reciprocable in the cylinders respectively, reactance means for the plunger, iiuid ducts in said barrel connected with said cylinders respectively, each duct being continuously in communication with its associated cylinder, said barrel having valve ports connected with the ducts respectively, valve means in valving cooperation with said ports, said barrel having an axial bore coaxial with the axis in rotation of the barrel and extending entirely therethrough from end to end, and being openat the ends for accommodating the work piece to be operated by the machine, an end portion of the barrel providing the spindie of the machine, and means for supplying pressure to said motor for driving the same.

3. In a rotary spindle machine, a casing, a rotary, radial plunger, hydraulic motor carried in the casing, said motor comprising a rotatable barrel, radial cylinders therein, plungers reciprocable in the cylinders respectively, reactance means for the plungers, iiuid ducts in said barrel connected with said cylinders respectively, each duct being continuously in communication with its associated cylinder, said barrel having valve ports connected with the ducts respectively, valve means in valving cooperation Awith said ports, said barrel having an axial bore coaxial with the axis in' rotation of the barrel and extending entirely therethrough from end to end, and being opened at the ends for accommodating the work piece to' be operated by the machine, an end portion of the barrel providing the spindle of the machine, the end walls of the motor casing having aligned passages aligned withlthe passage through the barrel and the spindle portion of the barrel extending therethrough, antifriction radial and axial thrust bearings mounted in the casing and supporting the barrel for rotation therein, said sets of bearings being coaxial with said axial bore of the barrel and constraining the barrel to substantially fixed axial position, and means for supplying pressure uid to said motor for driving the same.

4. In a rotary spindle machine, a hydraulic motor, comprising a casing, a rotatable barrel, axially spaced bearings, means in the casing rotatably supporting said barrel in fixed radial and axial positions, said barrel having Van enlarged diameter portion between said bearings, a plurality of radial cylinders in said enlarged portion, plungers reciprocable in said cylinders respectively, reactance means for said plungers and cooperable therewith for rotating the barrel, said barrel having a valve portion, longitudinal ducts in the barrel connected with the cylinders respectively, port ducts in the barrel connected respectively to said ducts and opening radially outwardly through said valve portion of the barrel, a valve portion in the casing surrounding and iitting the barrel valve portion and having a fluid inlet port and a fluid discharge port with bridges intermediate said ports for successfully cooperating the port duct openings with the casing ports consequent upon rotation of the barrel, said casends for accommodating the workpiece to be operated by said machine, and for permitting axialmovement of the work piece relative to the spindle during operation.

, 5. In a rotary spindle machine, a pair of hydraulic motors spaced axially apart, each of said motors comprising a rotatable barrel, cylinder and piston assemblies respective to the barrels, and adjustable reactances for the assemblies of the respective motors, valve means respective to said barrels and in valving cooperation with the cylinders thereof, said barrels being coaxial and independently rotatable about the common axis, each of said barrels having an end portion providing a rotary spindle integral with the associ- 'ated barrel and extending toward the other barrel, and each of said barrels having an axial passage extending entirely therethrough and open at both ends and coaxial with the corresponding passage in the other barrel, whereby a dual spinfor receiving uid, `and having a pressure conduit,

a rotary radial plunger hydraulic motor carried by the casing, and a high pressure conduit connecting the hydraulic motor and pump for supplying operating iiuid to the motor, and a low pressure conduit connected to said motor and discharging into said sump.

i 7. In a rotary `spindle machine a supporting casing for the machine, a hydraulic motor comprising a rotatable` barrel, a spindle coaxial withthe barrel and directly drivingly connected thereto, a driving motor mounted in said casing and having a drive shaft extending from each end of the driving motor, aA hydraulic variable delivery pump directly connected to one end of the driving motor shaft for driving thereby, and connected hydraulically to said hydraulic motor, another hydraulic variable delivery pump directly connected to the opposite end-of said driving motor shaft, a hydraulic motor hydraulically connected with said other pump, and means driven by said last mentioned hydraulic motor for controlling the feed of the machine during operation of the first mentioned hydraulic motor.

8. A hydraulic motor for a rotary spindle machine comprising a casing, a rotatable barrel in said casing and having a large diameter portion intermediate its ends, a plurality of radial cylinders in said enlarged portion, plungers reciprocable in said cylinders, reactance .means for said plungers, and cooperable therewith for rotating the barrel, said barrel having longitudinal ducts communicating with said cylinders respectively. said barrel having a reduced diameter portion adjacent the large diameter portion, said reduced portion -having a circumferential valving surface, said ducts having openings respectively in said valve surface, a valve port insert in said casing, and having a fluid inlet port and a uid discharge port, and bridges intermediate the inlet and discharge ports, said insert tting around said surface for successively, co-operating the ducts with the inlet and discharge ports of the insert y `consequent upon rotation ,of the barrel, aligned reduced diameter portions at its ends extending from within the casing outwardly through said l openings to the outside of the casing and providing a rotary spindle integral with the barrel, said barrel having an axial passage entirely therethrough and open at the ends through said end of portions for accommodating the work piece to be operated by said machine, and sets of antifrction radial and axial thrust rollers on each reduced diameter end portion of the barrel and mounted in the casing and constraining the barrel to iixed axial and radial position therein while rotatably supporting the barrel.

9. The combination with a machine employing a rotary spindle, of a rotary hydraulic motor including a rotatable barrel, a reactance, plunger and cylinder assemblies, and valve means for the assemblies, a spindle coaxial with the barrel and connected thereto for rotation therewith, and anti-friction bearings common to and supporting both said barrel and spindle. y

10. In a machine tool apparatus employing'a rotary spindle, a hydraulic motor comprising a barrel having an axial passage therethrough and a coaxial spindle on one end of the barrel having a coaxial passage extending entirely therethrough and into the barrel passage, whereby thework piece connected to the spindle may extend through the spindle and barrel, said barrel having radial cylinders, plunger assemblies in the cylinders, a reactance for the plunger assemblies, valve means in valving cooperation with the cylinders, hub

portions on the barrel coaxial with the barrel i passage, a casing for the motor, axially spaced sets of tapered` anti-friction bearings in the casing and engaging the said hub portions for rotatably supporting the barrel and spindle for rotation about said axis, and means for moving said sets of bearings axially with respect to each other for compensating for wear and radial slackness of the bearings and maintaining said spindle accurately positioned.

11. In a machine tool apparatus, a spindle, an adjustable stroke, reversible, hydraulic motor coaxial ,with and connected to the spindle for rotating the spindle about the axis of rotation of the motor, means for adjusting the motor stroke, a prime mover for supplying power for operating the motor, and a hydraulic fluid variable displacement pump operatively interposed between and connected to the prime mover and motor, and means for adjusting the displacement of the pump,

- whereby the power delivered to the motor and spindle is controlled, and the speed of the motor is controlled independently for a given power delivery from the pump.

12. In a machine tool apparatus, a spindle, a multi-stage hydraulic motor means having a plurality of independently adjustable stages and operatively connected to the spindle for rotating the same, a prime mover for supplying power, hydraulic pump means operatively interposed between the prime mover and motor means tor supplying operating fluid to the motor means, and means operatively associated with the hydraulic motor means to vary the iluid capacity of the stages thereof, wherebyV speed and torque combinations of the spindle are controlled.

13. In a machine tool apparatus, a spindle, a reversible variable displacement multi-stage radial plunger hydraulicimotor coaxial with and connected to the pintle for rotating the spindle, a prime mover for supplying power for operating the motor, and a hydraulic fluid variable displacement pump operatively interposed between and connected to the prime mover and motor, means nsl for adjusting the displacement of the pump whereby the power delivered to the motor and spindle is controlled, and means operable independently of the said means for adjusting the displacement of the stages of the motor, for effecting various speeds, and torques for each delivery of the pump throughout a constant horsepower cycle.

. 14. In a machine tool apparatus, a spindle, a reversible, variable speed, constant horsepower cycle hydraulic transmission means for driving the spindle and comprising a multi-stage reversible, variable stroke hydraulic motor in driving relation to the spindle, the stages of said motor being of different sizes and capacities from each other and being independently adjustable, a prime mover for supplying power t'o the motor, a uid pump operatively interposed between the prime mover and motor, and means directly connecting the pump to the stages of the motor, whereby theA motor stages can be operated independently and concurrently for eiecting variable speed and constant horsepower output of the spindle.

15. In a machine tool apparatus, the combination with a pair of axially aligned spindles, of independently operable hydraulically driven means coaxial withl and drivingly connected to the spindles respectively for rotating the spindles, and means for supplying operating uid to the hydraulic means.

16. In a machine tool apparatus of the character described including a carrier, means mounting the carrier for movement to dilferent positions, a driven variable displacement' reversible hydraulic transmission mechanism operatively drivingly connected to the carrier to operate the carrier for moving the carrier and a variable delivery hydraulic transmission means drivingly connected to theA spindle for driving the same independently of the rst mentioned transmission.

17. In a machine tool apparatus of the character described including a rotary spindle, a carrier, means mounting the carrier for movement to different positions, mechanical means flrivingly connected to th'e carrier for moving said carrier when the mechanical means is driven, a prime mover, a hydraulic pumpmember driven by the prime mover, a hydraulic motor member operatively connected to the pump member and to the mechanical means for transmission of power from the pump member to the mechanical means, and

, means to adjust the capacity of one of said members, and a driven hydraulic variable speed transmission independent of said rst transmission means operatively comiected to the spindle for driving the spindle.

18. In a machine tool apparatus ofthe character described including a carrier, means mounting the carrier for movement to diierent positions, drive means for driving said carrier, a hydraulic pump mechanism, means for driving the pump mechanism, and a reversible, variable displacement rotary hydraulic motor operatively connecting the pump mechanism and drive means.

19. The combination with an apparatus employing a rotary spindle, a carrier and a prime moving means, of means including a variable displacement, reversible, hydraulic transmission operatively drivingly connecting the prime moving meansI and` carrier, and hydraulic transmission means operable independently of the rst hydraulic transmission means drivingly connecting the prime mover means and spindle.

20. In a rotary spindle machine, a support, a rotary, radial plunger, hydraulic .motor carried by said support, said motor comprising a rotatable barrel, radial cylinders therein, plungers reciprocable in the cylinders respectively, reactance means for the plungers, valve means in valvingcooperation with said cylinders, a portion of the barrel coaxial with the axis of rotation of the barrel providing the spindle of the machine, and means for supplying fluid pressure to said motor for driving the same,

2l. In a rotary spindle machine, a support, a rotary, radial plunger, hydraulic motor carried by said support, said motor comprising a rotatable barrel, radial cylinders therein, plungers reciprocable in the cylinders respectively, reactance means for the plunger, iluid ducts in said barrel connected with said cylinders respectively, each duct being continuously in communication with its associated cylinder, said barrel having valve ports connected with the ducts respectively, valve means in valving cooperation with said ports, an

end portion of the barrel providing the spindle of the machine, and means for supplying pressure to said motor for driving the same.

22. In a rotary spindle machine, a casing, a rotary, radial plunger, hydraulic Amotor carried in the casing, said motor comprising a rotatable barrel, plunger and cylinder assemblies carried by the barrel, reactance means for the assemblies, valve means in valving cooperation with said assemblies, anti-friction radial bearings mounted in the casing and supporting the barrel for rotation therein, said sets of bearings being coaxial with.the axis of rotation of the barrel and constraining the barrel to substantially fixed. radial position, a rotary spindle rigidly carried by the barrel at one end and extending outside of the casing and coaxialwith the bearings for support thereby, and means for supplyingpressure iiuid to said motor for driving the same.-

23. In a rotary spindle machine, a casing, a rotary, radial plunger, hydraulic motor carried in the casing, said motor comprising a rotatable barrel, plunger and cylinder assemblies carried by the barrel, reactance means for the assemblies, valve means in valving cooperation with said assemblies, anti-friction radial and axial thrust vbearings mounted in the casing and supporting lsaid motor for driving the same.

24. In a rotary spindle machine, a pair of hydraulic motors spaced axially apart, each of said motors comprising a rotatable barrel, cylinder and piston assemblies respective to the barrels,

and adjustable reactances for the assemblies of.

the respective motors, valve means respective to said motors and in valving cooperation with the cylinders thereof, said barrels being coaxial and independently rotatable about the common axis, and coaxial rotary spindles rigid with the barrels respectively, each spindle extending toward Vthe opposite barrel, whereby a dual spindle machine is provided.

25. In a rotary spindle machine,- a spindle, a rotary hydraulic motor drivingly connected thereto, a hydraulic pump connected hydraulically to said hydraulic motor, another hydraulic miA operation of the first mentioned hydraulic motor,

and means for -driving said pumps.

26. In a rotary spindle machine, a rotary hydraulic motor, a spindle drivingly connected thereto, another hydraulic motor, means driven by said last mentioned hydraulic motor for controlling the feed of the machine during operation of the first mentioned hydraulic motor, pump means for motors respectively, and a common drive for driving said pump means.

27. In a rotary spindle machine, a hydraulic motor including a rotatable barrel, a spindle drivingly connected thereto, a driving motor having a drive shaft extending from each end, a hydraulic pump directly connected to one end of the driving motor shaft for driving thereby, and connected hydraulically to said hydraulic motor, another hydraulic pump directly connected to the opposite end of said driving motor shaft, a hydraulic motor hydraulically connected With said other pump, and means driven by said last mentioned hydraulic motor for controlling the feed of the machine during operation of the first mentioned hydraulic motor.

28. 'I'he combination with a machine employing a rotary spindle, of avvariable speed rotary hydraulic motor including a casing, a barrel, anti-friction bearings at each end of the barrel rotatably supporting the barrel in the casing, and said barrel extending through the casing at one end and providing the spindle of the machine.

29. In a machine toolapparatus employing a rotary spindle, a hydraulic motor comprising a barrel, a coaxial spindle on one end of the barrel, a reactance, piston and cylinder assemblies interposed between the barrel and reactance, valve means in valving cooperation with the assemblies, hub portions on the ends of the barrel,

a casing for the motor, axially spaced sets'of tapered anti-friction bearings in the casing and engaging the said hub portions for rotatably supporting the barrel and spindle for rotation about said axis.

30. In a machine tool apparatus employing a vrotary spindle, a hydraulic motor comprising a barrel, a coaxial spindle on one end of the barrel, plunger and cylinder assemblies carried by the barrel, a reactance for the assemblies. valve means in valving cooperation with the assemblies, hub portions on the barrel, a casing for the motor, axially spaced sets-of tapered anti-friction bearings in the casing and engaging the said hub portions for rotatably supporting the barrel and spindle for rotation about said axis, and means for moving said sets of bearings axially with respect to each other for compensating for wear and radial slackness of the bearings and maintaining said spindle accurately positioned. l3l. In a machine employing a rotary spindle, a variable speed rotary radial plunger hydraulic motor having a cylinder barrel, said barrel having an axial passage extending entirely therethrough and open at both ends, a spindle directly connected to the barrel in coaxial relation therewith and for rotation therewith and having an axial passage aligned with and forming a continuation of the passage in the barrel.

32. In 'a machine tool apparatus employing aA rotary spindle, a hydraulic motor comprising a pair of co-rotatable rotors,v piston and cylinder assemblies operatively interposed between the rotors for driving the rotors, valve means in valving cooperation with the assemblies, means for supplying hydraulic fluid pressure to said motor, and a rotary spindle coaxial with one of said rotors and directly drivingly connected thereto for rotation therewith about the axis oi rotation of the rotor to which connected.

ELEK K. BENEDEK.\

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